High differential pressure, low torque precision temperature control valve

ABSTRACT

A high differential pressure, low torque precision temperature control valve is disclosed herein. This valve is trunnionated with stem components that are separable from the plug for ease of maintenance and manufacturability and thus reducing the need to remove the entire plug and sealing assemblies in the field. Field repair of stem sealing devices can be accomplished inline . The stem design can be smaller in diameter with smaller bearing surfaces than would be anticipated creating a lower requirement of torque to rotationally transposition the plug within the fluid chamber while under high pressure. This valve&#39;s lower trunnionated stem is stationery reducing the problems associated with o-ring failure and leakage problems with objects that rotate. Due to the design of the orifices in the plug, this valve is capable of repeatability at lower opening ranges than prior art valves and reduces jetting, caviation and erosion often associated with lower opening ranges. Sealing devices are tensioned onto the plug through the use of non-metallic o-rings reducing wear and friction issues thereby further reducing the torque requirement to adjust the valve. The throughports of the plug in this valve are designed such as to create an equal percentage characteristic that does not exceed prescribed linear flow characteristics and provides a relatively constant total combined C v  over the travel range of the plug.

RELATED APPLICATIONS

This application claims benefit of prior filed co-pending provisionalapplication No. 60/767,152 entitled “High Differential Pressure, LowTorque Precision Temperature Control Valve” filed on Mar. 7, 2006 in thename of David B Keiser, said provisional application being herebyincorporated by reference as if fully set forth herein.

FIELD OF THE INVENTION

The specific field of the present invention relates to valves used tocontrol the temperature of specific areas in buildings through theregulation of flow of chilled or heated fluids through air handlingdevices. Due to this inventions characteristics, it has applicationsthroughout many fields where precision control of fluid flow is desired.

BACKGROUND OF THE INVENTION

The background of this invention delves into the arena of valves used tocontrol the flow of fluids, especially water. Water being a unique fluiddue to it's noncompressability and it's ability to be present in 2 formsat room temperature (liquid and vapor). Emphasis has been placed onusing valves in piping structures as a means for isolating or shuttingoff flow to particular areas. Heating and cooling within climate zoneshave been controlled by starting and stopping fluid control into pipingstructures, with the associated pumps often cycling with the valves.With the costs of energy rising, current emphasis is on using valves toact as precision temperature controllers, regulating the flow of chilledor heated water into and out of piping structures, reducing the load onthe pumps and heating and cooling units thereby decreasing energydemands, while maintaining properly controlled climate zones. Therefore,the type of valve necessary for this application needs to possess uniquecharacteristics.

There are basically two types of valves used in the application of waterhandling; those using a vertical displacement of the sealing mechanismand those using a horizontal or rotational displacement of the sealingmechanism.

Vertically displaced valve include globe and gate valves, where thesealing member either plunges into a slot or where a plug is compressedonto a seat. Both devices have similar operating characteristics andalso have similar problems. The sliding stem of the valve moves verticalthrough sealing o-rings and packing glands. The sliding stem movementtends to drag along creating leaks thereby shortening the life of thesealing system. In order to prevent this leakage, more sealing andpacking glands are used overly constraining the stem movement effectingthe controllability of the valve. Due to friction damage, these o-ringsand packing glands require frequent maintenance and replacements.O-rings are best used for rotational sealing application and are oftenused as wipers to prevent contamination, but often roll up and ceasewhen subjected to vertical motion, especially when subjected to a largepressure difference between the sealing surfaces of the O-Ring. Highpressure is also to the cause of valve stem blowout, as there is littleto protect the valve stem from acting in the normal vertical manner,only escaping the parameters of the valve stem run. As there are manyturns necessary to move the valve between it's open and closedpositions, more control can be exhibited, but these many turns also leadto hysteresis and deadband as there is a range through which an inputsignal can be varied, upon reversal of direction, without initiating anobservable change in the output signal. This sensitivity or mean staticgain is compounded by hysteresis of the valve causing inaccuracy of thecontrol of the valve, especially in the presence of high pressure whichcauses the sealing member to be more difficult to position. At higherpressures striction can also occur. Striction is a combination of stickand friction, where a force large enough to overcome the striction ofthe valve at high pressure is too great to create a small amount ofchange. Striction along with the hystersis can cause a controller tocycle many times trying to achieve the proper setting. Verticallydisplaced valves are also difficult to control in multiple portconfigurations. It is almost impossible for both plugs to seatsimultaneously or open to exactly the same location with one controllerfor 2 or more ports. Studies have shown that there can be up to a 20%overflow at 60-70% of opening between the ports, causing increasedenergy costs for pumping.

One of the most damaging forces that can destroy valves and thedownstream piping associated with the piping system is cavitation.Cavitation is the noisy formation and subsequent collapse of water vaporformed when the pressure of a liquid drops below its vapor pressure atthe vena contracta and then recovers to a pressure level above it'svapor pressure downstream of the valve. The vena contracta is theconstriction part of the valve when the valve is throttled at the lowerranges of openness. The fluid on the open side of the valve attempts to“jet” past the opening of the valve in a minimal degree of openness.This is especially prevalent in vertically displaced valves as there isa longer amount of time needed to open the valve including a longer timeperiod where cavitation can take place. This cavitation in high pressuresystems can destroy the sealing member of the valve and also causes highpressure jets of fluid to directly impinge on downstream valves andpiping system.

Horizontally displaced or plug valves are possibly the oldest type ofvalve is use today, dating back to the ancient ruins of the early Romanwater systems. The plug valve has a rotating plug, through which apasssageway is defined allowing fluids to flow when the passageway isunobstructed by the walls defining the valve seat. The two main designsin use today in the high pressure applications are segmented eccentricand through hole plug valves. Segmented refers to the fact that asegment or section of the plug is removed characterizing the flow.Eccentric refers to the fact that the axis of rotation is not along theaxis of the flow of the fluid, causing a leverage force upon the closingof the valve along with allowing the segment to swing clear of the wallsof the valve during opening and closing reducing friction, minimalizingwear. Unfortunately, due to it's eccentric characteristic, the presenceof high pressure increases the amount of force needed to open the valve,and due to it's segmented design, a high degree of caviation is presentwhen the valve is throttled close to the closed position. This jet offluid can actually be more harmful than with vertically displaced valvesas the shape of the segment can form a lethal jet of high pressure waterpast the valve without any obstacles in the valve itself. The pressuredifference between the high and low side of the valve in this throttledposition may also suck the plug into the seat. The high pressure canalso cause the segmented portion to pop out of the seat, causing a jumpin the flow. Eccentric plugs are not suitable for multiple outlet portconfigurations as the eccentric positioning for one opening will not besuitable for other openings at the same time, making complete shutoffimpossible to obtain.

The other plug valve is a through hole or ball valve. The installed flowcharacteristics of a normal ball valve exhibits a non-linear equalpercentage relationship of how the flow in the system changes relativeto changes in the valve opening. Ball valves are generally referred toas quarter turn valves as they only require one quarter of a turn tofacilitate a fully open state to a fully closed state. Typical ballvalves act as quick opening valves where 15% of opening of the valve canequal roughly 50% of the flow. This large amount of fluid passingthrough such as small opening causes jetting of the fluid and higherheat transfer through the coil, resulting in higher energy consumption.Caviation, that results due to the jetting also has a higher potentialto damage than would be found in globe or gate valves. It is verydifficult to control below 30% of opening as the amount of fluid flow isnot directly relational to the percentage of the opening of the valve.Normal ball valves optimally work between 30 to 70% of the openingpercentage and exhibit sluggish behavior beyond 70% opening. Somemanufactures have designed inserts for the throughhole portion of theplug, such as Series CPT Characterized Seat Control Valves manufacturedby Worcester Controls. Unfortunately, high pressures will cause theseinserts to break or blow out under the pressures as their constructionis less sturdy under the pressure than the surrounding plug material.

High pressures also cause high degrees of torque to open the valve. Thisis due to the fact that the plug or ball floats in the valve body as itis only suspended by an upper stem. In high pressures, the ball isforced upon the o-rings that prevent leakage of the valve. These highthrust loads on the o-rings cause o-ring wear due to the friction of theball against the o-ring during the turning of the ball under pressure.This friction can also lead to deadband, as the amount of forcenecessary to start the movement of the ball can not be stopped fastenough for minor changes in flow. Some manufactures have created sealingsystems where o-ring are pre-loaded in tension against the ball though aseries of metal springs, so that the o-rings will always be in contactwith the ball as disclosed in U.S. Pat. No. 4,292,989 issued toCazzaniga et al on Oct. 6, 1981 and in U.S. Pat. Nos. 5,624,101,5,542,645 and 5,494,256 issued to Benson.

Another problem with the current prior art of quick opening valves isthe effects on the efficiencies of the coils or piping systems that thevalves are intended to regulate. One application of the valve is tocontrol the amount of fluid flowing into coils of heating and coolingsystems. Current state of the art valve cause inefficient heat transfersby causing a large percentage of heat transfer or flow with only aminimal opening of the valve. This lack of fine control at the lowerpercentage of valve opening requires the continual cycling of heatingand cooling systems, further exacerbating the wear and destruction ofthe sealing components of the valve.

In low flow, high pressure situations, the difference in pressuresbetween the high side and the low side of the ball can create a venturieffect on the low side of the ball, sucking these extended o-rings outof position. Some manufactures have designed a trunnion apparatus tosupport the ball from the upper and lower extremes. This trunnion designincreases the number of o-rings as the stems are incorporated into theactual ball and the entire unit moves. Repeated actuations of the valvewill cause o-ring and packing gland wear as with the verticallydisplaced valves leading to leakage and maintenance issues. This createsproblems as the entire ball and stems must be removed as one to replacethe o-rings on the stems thereby causing re-assembly issues with thepresence of the o-rings that surround the actual ball itself. The costof casting and machining of these stem and valve apparatuses is veryhigh and tolerances are very small.

As described, there are problems with the current state of the industryinvolving precision control of valves. Leakage through worn or displacedo-rings causes false reading in the control systems causing energy to bewasted in powering the pumps and in the actual piping system as well.These false reading cause fluxations in temperature causing discomfortto the users, along with the environmental concerns of corrosive ortoxic fluids escaping through failing o-rings and valves. To combatleakage, more o-rings and packing glands are required which increasesfriction or striction. This friction requires more torque from theactuators and more power consumption, or operators are forced intolarger more expensive actuators for the valves. Friction also causesmore problems when combined with the naturally occurring deadband andhysteresis in valves. Poor flow characteristics causes erosion of thevalve members through the effects of caviation, inaccurate controlvariables and non-linear equal percentage flow relationships.Compatability of low flow abilities of various valves prevent properbalancing and utilization of the piping system, that the valves wereoriginally designed to control.

It would be advantageous to have a valve that would be able to withstandhigher pressures while maintaining a low amount of torque required forit's operation, along with the inherent ability to operate at lower flowrates without the damaging effects of caviation and erosion. It would beadvantageous to have this valve be maintainable without large scaledisassembly, whilst the sealing member is restrained from movement. Itwould be advantageous to have a investment casted trunnionatedspherically shaped plug valve with separable stems in a modular designdecreasing assembly and manufacturing time, as a hollow ball can besubjected to minimal machining and preparation reducing fatigue andinduced stresses on the actual ball. It would be advantageous to haveintegral with the plug equally shaped parabolic openings symmetricalabout the directrix of the parabola, said openings being diametricallyopposed juxtapositioned along the other side of the plug, whereby thesmaller orifice or vertex of one opening is opposite the larger or apexorifice of the other opening. It would be advantageous to have a thirdsuch opening or more along the surface of the ball, to facilitate agreater number of ports for the valve. It would also be advantageous tohave floating sealing members that are restricted in their movement,restrained into a specific space that will be not be effected by thepresence of a high differential pressures on either side of the plug. Itwould be advantageous to have this trunnionated plug which is integrallyenhanced with parabolically shaped flow paths, which is sealed withrestrained floating o-rings to be placed within a valve housing wherelow amount of torque is required to precisely control temperaturethrough the control of flow of fluids throughout piping systems.

It is an object of this invention to create a plug valve that istrunnionated with separable stem components.

It is an object of this invention to provide a plug valve with stems ofsmaller diameter that will require smaller bearing surfaces creatingless friction.

It is an object of this invention to provide a plug valve with astationery lower stem to reduce o-ring wear and associated leakageissues.

It is an object of this invention to provide a plug valve that does notproduce high velocity jets of fluids when valve is opened a smallpercentage, whereby the jets of fluid cause venturi effects that candislodge o-rings from their seats, damage piping system from caviationand erosion to the ball valve components.

It is an object of this invention to provide a plug valve that has thecapacity of up to 3000 Gallons per Minute and pressure differentials upto 100 psi but yet has the torque requirements of much smaller valveswith minimal amounts of hysteresis.

It is an object of this invention to provide a plug valve wherebydisassembly, repair and cleaning in the field of usage is accomplishedwith minimal effort where ball stems, stem seals and packing glands canbe replaced without effecting the ball/o-ring interface.

It is an object of this invention to provide a plug valve wherebyo-rings contain non-metallic components thereby reducing the possibilityof corrosion, decomposition and failure.

It is an object of this invention to provide a plug valve whose inherentflow characteristics dictates that the C_(v) changes in an equalpercentage manner over the travel range of the valve.

It is an object of this invention to provide a plug valve with equalpercentage characteristics of flow and travel that does not exceed thatwhich would be expected in a true linear relationship contrary to thequick-opening prior art valves that open more quickly than would bepreferred in a linear equal percentage relationship.

It is an object of this invention to provide a plug valve that byretarding flow at lesser percentages of the travel range of the valve,thereby increases the efficiencies of the piping systems by creating amore linear relationship between valve opening percentage and percentageof heat transfer.

We meet these objectives with an approach as disclosed in the followingdetail description of the invention.

SUMMARY OF DRAWINGS FIGURES

In FIG. 1, a cross sectional view of a 2 port valve is shown with theball in the open position.

In FIG. 2, the inlet and body portion of the housing is removed to showthe ball and stem arrangement.

In FIG. 3, the inlet and body portion of the housing is removed and thesealing means is exploded out in this 2 port ball valve.

In FIG. 4, the detail of the lower portion of the ball and lower stemare shown where raceway is detailed.

In FIG. 5, a cross sectional view of the 2 port valve is shown in thefully opening position. In FIG. 6, the outside view of the 2 port valveis shown.

In FIG. 7, the ball is shown in cross-sectional and oblique views.

DETAILED DESCRIPTION OF INVENTION THROUGH DRAWINGS

The present invention will be detailed in relation to the aforementioneddrawings. All disclosure is representative of the best mode ofpracticing this invention but that it is assumed that those skilled inthe art will be able to practice this invention in other fields ofapplication, nor does this disclosure limit the construction of thisinvention to the parts herein disclosed. Applicant recognizes thatdevelopment of future inventions may lead to better parts than thosedisclosed, but the intent of this application is to show the bestavailable parts currently available by their fit, form and function totheir exclusive use by this application.

In the principal embodiment of this invention, FIG. 1 shows across-section of a valve that is atypical of the ones used in theaforementioned applications. The valve 1, consists of three mainsections, inlet 2, valve body 3, and outlet 4. Inlet 2 and outlet 4 inthis view are representative of the style of attachment means used inthis type of valve. Generally this type of valve is used in commercialor industrial application where iron pipe is present. Flange 5 is shownis one method of accomplishing the attachment means for this valve 1.Other methods can include welded, socketed, threaded, brazed andsoldered attachment means are not shown here. This valve is not limitedto a specific attachment means on the inlet nor on the outlet side ofthis valve 1 nor does the inlet and outlet portion need to have the sameattachment means. Valve body 3 functions with various attachment meansand it's construction shall be appropriate to the pressures and flowrequirements of the system. Outlet 4 in this figure is shown as asingular outlet, but this does not limit this invention to a singleoutlet. Multiple outlet configurations are desired for this valve.

Valve body 3 is positioned between the outlet 4 and inlet 2 along thesame central axis. Inlet 2 and outlet 4 are fastened togetherinterfacing valve body 3 between inlet 2 and outlet 4 using multiplethreaded shafts 21 terminated with threaded nuts 22 and locking washers22W on each end of shaft 21 through fastening plates 23 and 24. Inlet 2has exterior opening 206 which defines the initial inlet bore 207 whichtapers down to entrance bore 208 and terminates at entrance 209.Entrance 209 defines the passageway 230 for the fluid as it enters or isshut off from entering the plug. In this invention, the plug is aspherical ball 13. Exit 409 likewise defines the passageway 430 forfluid that exits the valve through ball 13. Interior face 210 of inlet 2defines one edge of chamber 11. Chamber 11 is defined by face 210, valvebody 3, and face 410. Slope 212 and slope 412 are defined by thediameter of ball 13 and is positioned such as not to interfere with therotation of ball 13. Interior of face 210 lies slope 212 whichterminates on landing 213 which is the upper portion of flange 214. Inaccordance with the teachings of U.S. Pat. No. 6,948,699 issued toKeiser, flange 214 is to contain the axial displacement of sealingmember 14 along raceway 215 to prevent disengagement with ball 13 due tohydrodymanic forces present when ball 13 is opened a small percentage oftravel and high fluid pressure on the inlet side causes the sealingmember to be pulled to the low pressure side of the valve. Flange 214also aids in the assembly of valve 1 as it allows a preload of tensionfrom linear stroke o-ring 15 while maintaining it's position withinraceway 215. Keiser also taught the use of linear stroke o-ring 15 as ituses a conventional double D style of o-ring which is elliptical inshape. Use of conventional o-rings eliminates the need for expensivemetal springs and also eliminates the need for extra o-rings to protectthe metal springs from corroding. Linear stroke o-ring 15 also serves asa seal preventing fluid from being present under sealing member 14eliminating leakage. The composition of sealing member 14 is polymermaterial, preferably polytetraflouroethylene, whose wear characteristicsinclude self-lubricity, toughness and chemical compatibility with fluidspresent.

FIG. 4 details the dynamics of the interface between sealing member 14,linear stroke o-ring 15 and raceway 215. Sealing member 14 has a curvedsurface 20, mating specifically with the outer diameter of ball 13, andis in constant contact with ball 13. Linear stroke o-ring 15 ispreloaded under pressure into it's containment barriers. This preloadedtension in compression forces sealing member 14 onto positive contactwith ball 13. Sealing member 14 has a lower portion 14B, opposite curvedsurface 20, which is shaped to travel along raceway 215 with a relief14R cutout to accommodate termination at flange 214. Curved surface 20is the only sealing surface along ball 13. Linear stroke o-ring 15 isencased in groove 118, defined by the lower shelf 217 and upper shelf219 whose leading edge is beveled to facilitate the assembly of theo-ring 15 into groove 218. Anterior Stop 220 defines the rearwardtermination of the travel of sealing member 14 along raceway 215. Linearstroke o-ring 15 is composed of materials suitable for chemicalcompatibility, ductility and repeated compressibility. In thisinvention, a synthetic compound of rubber is used. In this invention,groove 218 is perpendicular to face 210, but this invention can beaccomplished by transposing groove 218 and flange 214 to opposite sidesof the raceway from their location in FIG. 1 so that groove 218 isparallel with face 210. Outlet 4 has similar layout characteristics asinlet 2 in the location of sealing member 14 along raceway 415, flange414, landing 413, stop 420 and linear stroke o-ring 15 within groove 418defined by shelf 417 and 419.

The best mode for creating ball 13 is investment casting, though otherforms of fabrication can be accomplished. After casting, only minormachining is necessary to finish the ball for a smooth exterior surface.FIG. 7 details ball 13 as having a defined top containing slot bus 54, abottom defined by opening 57 and a series of parabolic openings 51. Slotbus 54 contains slot 55 defined by the shape of the lower portion ofupper stem 70L. It is generally accepted that a rectangular slot isprescribed as provides a larger surface area and takes advantage of thetorsional stability of the stem material and increased surface area,though other shapes can be used such as Torx or hex. Slot 55 has cornersfinished to a tooling radius to facilitate an easier manufacturabilityand also to aid in the insertion of stem 70L into slot 55. Tolerancesbetween stem 70L and slot 55 are directly proportional to the amount ofdeadband of the valve. Bottom of ball 13 is defined by an opening whosecircumference 57 is large to facilitate the casting process, alsointerfaces with bottom stem interface 56. Bottom stem interface 56 is aseparate piece cast of the material as ball 13 where lip 58 contacts theouter diameter of ball 13 securing it's fit and preventing steminterface 56 from entering the interior of ball 13. Bottom bus 59protrudes from exterior surface of stem interface 56 and containingcircular slot 60, inside of which bearing surface 61 is forciblyinserted to bearing stop 63. FIG. 1 details the interface between slot60, bearing 61 and bottom stem 62. Bottom stem 62 is stationeryrequiring the bushing to be placed interiorly in slot 60. It is themodularity of this invention that makes it unique. The wear items areremoveable and are separable from the ball itself. Stems can bewithdrawn and o-rings are replaceable without interfering with the balland the sealing members that are left in place. Major servicing of thevalve can be done while the valve is inline, without the need fordisassembling the valve for the majority of repairs. Parabolic opening51 are in accordance with the teachings of U.S. Pat. No.5,937,890 issuedto Marandi, which has common-ownership with this application, whichstates that parabolic openings more accurately compensates for thearcuate or nonlinear path traveled by the parabolic opening 51 becausethe parabolic opening 51 provides a cross-section that projects acrossthe passageway 230 and 430 to obstruct the passageway 230 and 430 insubstantially equal percentage fashion as ball 13 is turned in aparticular degree of rotation. The apexes of the parabola 52 and 53 thatdefines parabolic opening 51 is mathematically calculable based on thedesired maximum flow of fluid exiting the valve. In this invention,parabolic opening 51 is laser cut directly into ball 13, as prior artinserts in the presence of high pressure can be either dislodged fromtheir mountings on the ball or be shattered when in static interferencewith the fluid flow separate from the ball. It is also unique to thisinvention that throughflow ports are juxtapositionally opposite anddiametrically opposed. Thus as ball 13 rotates into an opening position,the entrance parabolic opening 51 is at it's smallest aperture, wherethe exit parabolic opening 64 is at the maximum aperture. This diametricopposition reduces the jetting of fluids, while maintaining a relativeconstant C_(v). Prior art valves rotates the smallest aperture on boththe entrance and exit of their cylindrical throughports, causing ajetting of the fluids at high pressure. This arrangement of diameticallyopposed openings are juxtapositionally opposite of each other alongsimilar axis and diameters. The vena contracta is minimalized thusreducing the chances of caviation as the pressure drop is minimalizedand a higher recovery rate is realized. Valve surfaces are subjected toless erosion due to caviation and due to the parabolic shape, a smootherpercentage relationship is found that stays at or below a true linearpercentage relationship, allowing for greater precision and control ofthe fluid flow at 10-20% of opening, a critical area of non-operabilityfor prior art ball valves.

Bottom stem 62 enters through bottom stanchion 368 which is part ofvalve body 3. O-ring 69 is located in groove 240 which is part of theinterior portion of inlet 2 provides sealing between valve body 3 andinlet 2. Groove 440 provides a similar groove for the interface betweenoutlet 4 and valve body 3 whereby o-ring 69A is located therein.Exterior portion of bottom stem 62 is piloted into stem base 363 bypilot stem 364 preventing accidental dislodgement during assembly.Bottom stem primary o-ring 65 is located along the shaft of stem 62 andsecondary o-ring 66 is located aft of primary 65 for additionalprotection against leakage. Base 363 is attached onto exterior portionof stanchion 368 using attachment means 367.

Upper stem 70 is the principal rotational means for transferring thelocation of ball 13 within chamber 11. Upper stem 70 is machined out ofone piece of common circular rod stock into 3 distant areas, lowerportion 70L, body portion 70B and upper portion 70U. In this invention,lower portion of stem 70L is machined to be rectangular prior to beinginserted through slot 55. A stop may be incorporated into the design ofball 13 and slot 55 but optimal performance is achieved without thepresence of a stop allowing for minimal ball travel in the verticalplane should the need exist without placing compressive forces onto stem70 causing rupture of the stem. Upper stanchion 301 is located on theupper portion of valve body 3 and is integral therewith. Immediatelyadjacent to the exterior sides of valve body 3 is the inlet portion 2 onone side and outlet portion 4 on the other side. Groove 240 containingo-ring 69 provides sealing between the interface of valve body 3 toinlet 2 and groove 440 containing o-ring 69A provides the sealinginterface between valve body 3 and outlet 4. Anterior end of stanchion301 is immediately adjacent to post 54 of ball 13 and is separated frompost 54 to prevent wear and friction. At the anterior end of stanchion301, bearing surface 310 is located, being sufficiently long enough tosupport the thrust side loads experienced by ball 13 under the presenceof high pressure but short enough to allow for minimal frictionalforces. Upper stem body 70B is circular in nature has a length dependentupon the amount of torque to be generated by the actuator of the valve,using the laws of physics. At the exterior end of stanchion 301, bearingblock 311 is located. Bearing Block 311 is long enough to encapsulateprimary sealing gland 312 and secondary sealing gland 313. Exterior endof bearing block 311 is adapted to interface with anti-twist plate 315.O-ring 314 creates a seal between exterior end of bearing block 311 andexterior end of stanchion 301. Pinions 317 extend perpendicularly fromthe lower face of anti-twist plate 315 and slide into equal number ofpinion pockets 318. Anti-Twist plate 315 is covered by top plate 316which is attached through attachment means through to the exterior endof stanchion 301. Upper portion of stem 70U is shaped to receive anactuator. An actuator can be a manually adjusted handle or wheel or acontrolled pneumatic or hydraulic actuator socket as the means toactuate motion in the horizontal plane of ball 13. In the presentinvention, upper portion 70U is shaped into a square pattern to receivea square key. This arrangement of modular construction of the stem andball does not permit movement of the ball when subjected to highpressures. Contrary to U.S. Pat. No. 5,494,256 issued to Beson on Feb.27, 1996 where the ball is free to move the direction of the fluid flowto contact seat. Beson also discloses that the hole holding upper stemis larger than the hole holding the lower allowing for ball movementtoward the seals. In the present invention, the seals are floating andthe ball is stationery. Both Beson and U.S. Pat. No. 4,026,516 toMatousek issued on May 31, 1977 disclose ball and stem combinations thatare integral to each other. Matousek also prefers that the lower bushingby substantially larger than the height of the trunnion. This addedfriction causes wear issues and also requires a large diameter stem, asshown in Matousek, and torque to overcome the friction component.

It can be seen that maintenance on the wear portions of this valve canbe accomplished by either removing the lower stem 62 through stanchion368 or removing the upper stem 70 through stanchion 301. O-rings can bereplaced and stems assembled back into the respective posts within amatter of minutes, rather than having to disassemble the unit to removean integrated ball and stem assembly. Ball seals are left undisturbedwhen stem components are in need of maintenance. Prior art requires theresetting of ball seals as the ball and stem are removed togethercausing a great amount of labor and time to facilitate replacement ofsimple o-rings on the stems.

Outlet 4 has similar geometries of inlet 2 whereby fluid enters theinterior side of outlet 4 through entrance 409. Exit bore 408 increasesin diameter as it approaches the exit bore 407 and fluid exits throughthe exterior opening of 406 into the piping system. As with most plugvalves, the orientation of the valve is not critical for it'sperformance, so the outlet and inlet portions of the valve could be usedin opposite functions.

This valve has succeeded in achieving the objectives of this invention,and though only current technology exists, future technologies mayproduce materials and components that would accomplish these objectivein different or similar manners. These advances would be considered tobe within the spirit, scope and intent of this patent and the claimsherein disclosed

1. A high differential pressure, low torque precision temperaturecontrol valve comprising; a fluid chamber; a fluid acceptance passagewayand a fluid discharge passageway each having interior and exterioredges; a valve body, having upper and lower stanchions, where saidinterior edge of said fluid acceptance and said interior edge of saidfluid discharge passageways are axially disposed and appurtenant toopposite ends of said fluid chamber; an attachment means connected ontosaid exterior edge of said fluid acceptance and said fluid dischargepassageways; a plug centrally interposed therein said fluid chamber,spherically shaped, possessing an upper boss and a lower boreholecentrally disposed on the parameter of said plug along the vertical axisof said plug, and a set of orifices diametrically opposed,juxtapositionally opposite, along the parameter of said plug along thehorizontal axis of said plug, where said horizontal axis of said plug iscoincident with the horizontal axis of said fluid acceptance and saidfluid discharge passageways, said upper boss is adapted to receiverotational transpositional means for said plug, said lower boreholeadapted to forcibly receive a plate, said plate has externally mountedthereonto a lower stem receiving post; a two sided racewaycircumferentially described onto and near said interior edge of saidfluid acceptance and said interior edge of said fluid dischargepassageways, said raceway having a depth and a height component; acircumferential groove circumscribed within said raceway; a set ofnon-metallic sealing members, elliptical in profile, disposed withinsaid circumferential grooves; a set of polymer based seals, polygonal inprofile, in sustained contact with said plug, having a radiused face, alower frontal area, an upper frontal area, a flat bottom less in lengththan said depth component of said raceway, and an exterior side adaptedto receive a portion of said sealing member; an upper stem, superimposedinternally to said upper stanchion having an anterior and a dorsal end,where said anterior end is adapted to frictionally interface with saidupper boss of said plug, said upper stem providing rotationaltranspositional means to change position of said plug along saidvertical axis of said plug, said dorsal end of said upper stem isadapted to receive an actuator interface; and a lower stem, superimposedinternally, to said lower stanchion, stationaryily mounted to exteriorend of said lower stanchion and bearingly mounted into said lower stemreceiving post.
 2. A high differential pressure, low torque precisiontemperature control valve as in claim 1 where said raceway has installedthereon a containment ledge containing movement in the plane ofdecompression of said sealing member, said ledge to be no greater than adistance whereby said sealing member has not less than 10% compressionwhen said seal is in contact with said ledge.
 3. A high differentialpressure, low torque precision temperature control valve as in claim 2where said lower frontal area of said seal is adapted to interface withsaid containment ledge.
 4. A high differential pressure, low torqueprecision temperature control valve as in claim 1 where plane of saidsealing member decompression is parallel to horizontal axis of saidplug.
 5. A high differential pressure, low torque precision temperaturecontrol valve as in claim 1 where plane of said sealing memberdecompression is parallel to vertical axis of said plug.
 6. A highdifferential pressure, low torque precision temperature control valve asin claim 1 where an o-ring is placed along the interface of said valvebody to said fluid acceptance passageway, and said valve body interfacewith said fluid discharge passageway to prevent leakage.
 7. A highdifferential pressure, low torque precision temperature control valve asin claim 1 where said radiused face of said seal is coincident withouter radius of said plug.
 8. A high differential pressure, low torqueprecision temperature control valve as in claim 1 where major diameterof said elliptical profile of said sealing member is such as to maintainat least 10% compression whilst said plug is in contact with said seal.9. A high differential pressure, low torque precision temperaturecontrol valve as in claim 1 where said upper stem and said lower stemare adapted to receive o-rings to prevent leakage.
 10. A highdifferential pressure, low torque precision temperature control valve asin claim 1 where said orifices are two parabolically shaped curvessymmetrical about their directrix, apex of said curves aremathematically derived from and proportionally related to flowrequirements of valve, said apexes joined by radiused segment.